Variable delivery vane pump



May 9, 1944 y w. R. TUCKER 2,348,428 f VARIABLE DELVERY PUMP Filed Dec. 22.1qs9 8 Smets-sheet 3 Jan/DMU @WARREN RIQCKER Mays, `1944. Wn R TUCKER; 2,348,428

VARIABLE DELIVERY VANE PUMP` v Filed Dec. 22, 19:59 8 sheets-sheet 4 4 56 4 ATTORNEYS May 9, 1944 `w. RL TUCKER i VARIABLE DELIVERY VANE PUMP Filed Dec. 22, 1959 INVENTOR WARREN R.TUCI ER BYff x Arron/HYS Maya, l1944. w.- R. TUCKER 2,348,428

VARIABLE DELIVERY VANE PUMP Filed Dec. 22, 1959 e sheets-sheet e a l a 1 1 Jwuwm WARREN R. T ucKER,

May 9, 1944. w ER 2,348,428

VANE PUMP Patented MayfS, y1944:

' PATENT. OFFICE 9 This inventionV relates to a vanepumpor motor, and more :particularly to' a vase device which when employed as apumphas'variable delivery' and, correspondingly,when applied as a motor has variable speed. In this specification, the de. vice will be termed 4a' pump .but it is to be understood that the term "pump includes a motor since the devicecan be operated-'as amotor if fluid underpressur'e'is supplied toit. Accord'-A ingly, While the description-refers totherdevice' as a pump, it will be understood'that the :corresponding operation of the devicef asfa'motor with u appropriate 'changes in the terminology employed, is contemplated. The pump-of the present invention is particularly adaptedto the sup- .jplying of a liquid under pressure', but ity may-lie r'employed to compress a gas.' For exampl' the'ff device can be employed as an air compressor, or

forV vcompressing `other gases. The descriptionherein will relate particularly to devices which are especially adapted to the pumping of a -hydraulic liquid such as oil or the like, as for example `the hydraulic medium employed vin the operation of hydraulic presses and related mechanisms.

The principal-object of the present invention is to provide a vane pumpwhich is of simplified y construction, simple to assemble, and economi'- cal to construct, of increased mechanical ei 30 `the foregoing type wherein the ring or cylinder ciency whereby the power supplied makes available a larger amount of pressure'flud, and of reduced wear and maintenance; in a preferred embodiment, the pump is easily adjusted to take up such wear as occurs in the pump bearings. e

Another object is to provide a vane pump in Whichthe ring or cylinder which is .eccentricto the rotor and which is normally stationar'yin the conventional vane pumps, rotateswith 'the vanes and the rotor atv substantially the same speed as the rotor, thereby-eliminating the fric-V tion due to the vanes sliding von the innerl periphery of the ring as in the ordinary vane pump; since this peripheral friction between the vanes and the cylinder or ring is increased by the action of centrifugal force on the freely radially movable vanes, and therefore goes up as the square of the speed of the rotor, the elimina- 'tion of this friction by causing the cylinder to rotate with the vanes is an important factor in the increased efficiency and reduced wear of the vane pump of the present invention.

e Another object is tov provide-a vane pumpwhich if; capable` of making a variable delivery, the

vvariation in the delivery being eiiected in a simple and convenient manner, this variation cover- 1 the inlet or suction side.

ing the range from no delivery to the maximum delivery in an infinitely variable manner.

Another object isto provide a vane pump inV whichthe delivery is reversible in a simple and 5 convenient manner, `whereby the former inlet or suction side of the pump is converted to the prese sure side andthe former pressure side becomes .Still .another object is to provide avane pump which is capable of infinitely variable deliveryand which is reversible,d the pump being capable of infinitely variable delivery in either mode of operation.

Still another object is to provide a lpump in l5 which the 'output is reversi-ble by reversing the ldirection of rotation of the rotor, whereby the former inlet side of the pumpV is changed to a. pressure side without the necessity for shifting the ring of the pump;V this allows the pump to be manufactured in such mannerthat the shift ring is movable from the neutral position to the posi-4 tion of maximum delivery only` in onf.l direction.

Another-object is to provide a vane pump in which the side walls of the pump are xedly car- 2.5 ried by the rotoruand rotate therewith; this contributes materia y to the reduction of friction since the friction between the rotor and vanes and the side walls is eliminated.

Another object is to provide a vane pump of which the vanes contact is rollingly mounted, as for example, by being made the inner race of a roller or ball bearing, whereby the friction of the vanes against the ring-is greater than the rolling friction of the ring against its rolling mounting,

and, therefore, causes the ring to rotate with the vanes and rotor; in a preferred embodiment, the rolling mounting of the ring is made `movable so as to thereby vary the eccentricity of the ring with respect to the rotor and to thereby vary the assembly on the outside of said rotor and the distribution s1eeve, all of which move together and can be adjusted together within the casing,

. longitudinally of the casing to accommodate A4wear and slight movement in operation. In this manner, the pump is self-accommodating in its moving parts to varied conditions. of Voperation and to wear. Additionally, means is provided for adjusting the supporting bearings forrthis` complete assembly and for simultaneously movlng the rotor, its bearing assembly vand the disshaft of the main vide bearings for supporting the shaft of the pump rotor, which bearings support'the distribution sleeve in such a manner that the total diameter of the bearings is suiiicient to support the distribution sleeve in spaced relationship to the casing with a suicient clearance that any bending moment of the rotor shaft and of the distribution sleeve will not cause any binding between the sleeve and the Dump casing, but at the same time the clearance is so small that a substantially fluid-tight engagement is maintained, particularly when pumping fluids such as oil, where the viscosity of the oil in combination with the slight clearance provided is` sufficient to make a substantially fluid-tight seal and to lubricate the rotating distribution sleeve as it turns within the casing.

Fig. 12 is a section on the line |2 l2 of Fig. 1l looking in the direction of the arrows.

Fig. 13 is a fragmentary enlarged view of the left hand portion of the pump of Fig. 2, this view having the clearance between the left hand portion of the shaft and the pump housing greatly exaggerated for clarity.

Fig. 14 is a similar fragmentary enlargement of the middle upper portion of Fig. 2, showing in exaggerated form the clearances between kthe shift ring of the pump and the housing and between the right hand bearing and the supporting housing therefor.

General arrangement The pump ofthe present'. invention comprises a rotor. provided with 'radial ports leading from Still other objects of the present invention will more fully hereinafter appear and be readily apparent to those skilled in the art as the description proceeds.

In the accompanying drawings: y

Fig. 1 is a transverse section taken on the line I I of Fig. 2. of a pump embodying theprinciples of the present invention.

Fig. 2 is a longitudinal section taken on the line 2 2 of Fig. 1.

Fig. 3 is a transverse section on the line 3 3 of Fig. 2, looking in the direction of the arrows. Fig. 4 is a fragmentary longitudinal section of the pump in Fig. 2 equipped with a. pilot pump` driven by the rotor of the main pump and mounted at the 'left-hand end of the pump of Fig. 2, this pilot pump being constructed in accordance with the principles of the 4present invention; this view shows howreadily a pilot pump may be directly connected to the shaft ofthemain pump when the main pump is constructed in accordance with the present invention, because the whereas in previous constructions the pump shaft has been inaccessible from one side of the pump. Fig. 5 is a transverse section through the pilot pump shown in Fig. 4 on the line 5 5 of Fig. 4 looking in the direction of the arrows.

Fig. 6 is a transverse section similarv to Fig. l1 of a modified form of pump in which the pump cylinder rollingly engages rolling elements which are adapted torotate about a xed center through the intermediary-of a needle bearing; this view is taken on the line 6 6 on Fig..7.

Fig. 7 is a sectional view taken on the line 1 1 of Fig. 6.

Fig. 8 is a longitudinal sectional view through a modified form of pump which is vmodified from that shown in Fig. 1 by having ywhat is known as pintle valving.

Fig. 9 is a detailed sectional view on the line 9 9 of Fig. 8, and shows further details of the pintle valving.

Fig. 10 is a longitudinal section through a still further modification of pump which has been ymodified from the pump shown in. Fig. l by having the valving at the side plate of the pump instead of on the pump shaft; this construction is particularly adaptable where the pump shaft is g so small that the porting cannot'be accommodated therein without undulyweakening the pump shaft.

Fig. 11 isa transverse section on the line I l-H of Fig. 10, lookingin the direction of the arrows,

pump is readily accessible,

.15 which the side the lperiphery ofthe rotor to suitable valving mechanism associated with the rotor or with mechanism fixedly or integrally carried thereby for valving the ports in the rotor to the inlet side orto the pressure side of the pump. As the rotor rotates, the valving mechanism successively connects the successively presented ports in an appropriate manner so that the suction side of the pump is separated from the pressure side thereof. i

The rotor is provided between each pair of ports with a freely radially slidable vane. 'Ihese vanes define the suction and pressure chambers in the pump by cooperating-with the pump cylinder which is disposed around the rotor and vanes.

By shifting the eccentricity of this pump cylinder relative to the rotor, theamount or direction of delivery of the pump may be varied to suit the individual requirements.

yThe cylindrical ring of the pump is mounted so kthat it is freeV to rotate with theA vanes and the rotor carrying the same, the speed of rotation of the cylinder being substantially uniform and substantially equalling the speed of the rotor. In a preferred form, the cylinder is rollingly mounted by making it the inner race of an antifriction bearing such as a ball or roller bearing, whereby it is insured that the rolling friction of the cylinder with respect to the rolling elements of the bearing is much less than the friction between the vanes and the cylinder and consequently that the cylinder rotates with the vanes.

In a preferred form, the pump is made of the variable delivery type by making the outer race of the bearing just mentioned shiftable by mounting-it so as to be transversely slidable in the housing of the pump. This outer race thus becomes the shift ring and by shifting this ring the pump cylinder may be varied in eccentricity with respect to the rotor by the provision of any suitable means for moving the outer race or'shift ring transversely of thepump, whereby the amount or direction of delivery of the pump or both may be varied either manually or by suitable servopump are sealed by side walls which are fixedly mounted upon the rotor and which consequently rotate therewith. 'lhese side walls are slidable relative to the pump cylinder and thus allow it to continuously assume its new position without destroying the seal between the side plates and the cylinder. The relative movementl between thev side walls of therotor and the cylinder is very slight and the friction attendant thereupon is ex'tremelygsmall compared with the friction which is presentl in the ordinary vane pump in walls are stationary relative to the rotor and rotor vanes. Thus lthe pump ofy the present invention in addition to eliminating the frictionbetween the vanes and the cylinder also eliminates the friction between the rotor and.`4

vanes and the side walls of the pump.

From the foregoing, it will be seen that one of th'e principal features of the present invention is that ofhaving the pump cylinder rotate with the rotor; in aA preferred form, this cylinder is i rollingly carried on an anti-friction bearing and in a still more preferred form is carried' on a higher pairing (line or point contact) bearing in which rolling friction is present instead ofa low-V er pairing (surface contact) bearing in which sliding friction is present. Any other means of allowing the cylinder to rotate freely so that its friction of rotation is lower than that of the friction between the vanes and the cylinder may be employed. For example, as will become apparent, the cylinder' may be supported by and rollingly engaged with rollers which are free to rotate about a stationary pivot point and which themselves may be provided with suitable antifrictionbearings such as ball, roller, or needle bearings. It will further be seen as the description proceeds that the vanes are desirably truly radially disposed as distinguished from some vane pumps heretofore constructed in which vanes are mounted at an angle to the rotor. It will further be understood that suitable porting is `pro vided in which the porting holes ar'e large enough to prevent bubbling and other disadvantageous eects dueto too high a velocity of the oil and the like through the ports. Where the pump shaft is sufficiently large in diameter to accommodate ports of the required size, they may be disposed in the shaft, and where the shaft is relatively small, the porting may be exterior of the shaft in a manner which will hereinafter appear.

i' Preferred form In the preferred form shown in Figs. 1 to 3,

themain housing of Ythe pump is designated by reference numeral I, this housing lbeing closed vby the cover plate 2 which forms pari; of the housing and which is attached thereto by means of bolts 3. The pump shaft is designated asv 4 and is carried on a tapered roller bearing 5 mounted within a. reduced end portion 6 of housing I, and

by a similar tapered roller bearing 1 mounted within a hanged portion 8 of end plate 2. Bearing 5 comprises the inner race 9 which is fixedly mounted around an enlarged portion I3 of shaft 4, and an outer race I| which is flxedly held within end portion `Ii of housing I. Correspondingly, the bearing 1 comprises an inner race |2 flxedly mounted around an enlargedportion I3 of `shaft 4, and an outer race I4 which is received within the flanged portion 8 of end plate 2 and is free t9 slide longitudinally but which ,is normally stationary relative thereto by reason ofV the frictional engagement therewith.l Outer race I4 is adapted to b e pressed Yinwardly by a member i5 engaged by an adjusting' member I6 which is threadably received within the outer portion of circular ange 8 and which is adapted. to be rotated by -the. insertion of a suitable sparner wrench into the recesses I1 therein.' In this way.

outer race I4 of bearing 1 maybe moved inwardly, causing a take-up of the wear inbearing 1 and causing inner race 9 of bearing 5 to be simultaneously moved leftwardly of Fig. 2, thereby taking up the wear in bearing 5., In this way, by one adjusting operation, the wear ofthe bearings 5 and 1 4may be vtaken up,

Til

Porting and valuing The rotor of the pump is designated as I8 and is formed integrally with shaft 4. As illustrated, this rotor lpis provided with twelve radially disposed ports |9 which extend inwardly from its periphery into communication with Corresponding .axial bores' 20 disposed in the enlarged shaft portion I0. These bores 20- merge with radial bores .2| in the left-hand end of shaft portion I0 as viewed in Fig. 2. As is seen from Fig. 3, these bores 2| are taken off divided fashion, a portion of them being in communication with a conduit 22 in casing portion 6 through an annular zone 23. Another portion of radial bores 2| is in communicationwith a conduit 24 at the bottom of casing portion 6 through an annular zone 25.

Vanes The rotor I8 vis provided with a plurality of vradial slots 26 extending inwardly from its periphery and located intermediate the ports I9'. Mounted slidably in these slots 26 are the vanes 21 which are of a length equal to the length of the rotor I8 and which'are of a width not greater than the depth of slots 26. In thickness, the

vanes 21 are almost equal to the thickness of slots 28 so that while the vanes are free to move radially with respect to the rotor 8, they are sealed with respect thereto by reason of their close fit therewith. These vanes are adapted to j be thrown radially outwardly as rotor |8 rotates by reason of the action Ofcentrifugal force until they engage the pump cylinder presently' to be described.

Pump cylinder The cylinder or ring is designated asv 28 and constitutes an inner race of the roller bearing. the rollers 29 of which roll upon the annular member 30 which is concentric withthe cylinder 28 and which constitutes the outer race of the roller bearing thus formed. The outer race 30.

and with it the rollers 29 and the cylinder 28. f

is shiftable transversely so as to vary the output of the pump, this being effected by making the shift ring 30 flat on its outer periphery on both the top and bottom as at 3|, this flat surface 3| slidably cooperating with flat portion 32 on the interiorV of the housing and at the top and bottom thereof. Transverse movement of shift ring 30 and corresponding movement of cylinder 28 is effected by the provision cf shifting pins 33 and 34 slidably disposed at the right andleft-hand of Fig. 1 within suitable bores provided therefor in casing I. `These pins 33 and 34 may be moved by any suitable means vnot shown,'such as manual means or suitable servomotor means. These pins 33 and 34 serve to positionthe cylinder 28 and to thereby determine its eccentricity with respect to the rotor ,I8 and the amount and direction of delivery into conduit 22 which is now the pressure conduit. At the same time, the lower portion of the pump in Fig. 1 is the suction side and causes .walls 36 and 31 is extremely small however befluid to be sucked in through conduit 24 which is now the suction or inlet conduit, thence through annular zone into the radial bores designated C in Fig. 3, thence longitudinally through the corresponding axial bores 28 and 5 through the rotor ports I9 which are designated D in Fig. 1 outwardly into the expanding'chamvbers formed by the vanes 21, the rotor I8 and the cylinder 28.

In order to seal the intake side of the pump 10 from the pressure side, those chambers in the pump which are not appreciablychanging in volume at the instant considered are sealed off in the vfollowing manner. These chambers are in communication with the horizontally dsl5 posed rotor. ports designated as E in Fig. 1. These ports E communicate with shaft ports F` in Fig. 3 and at the instant considered, these shaft ports F are sealed off by their engagement with dividing projections 35 formed on 20 the casing portion 6 intermediate of the annular zones 23 and 25 (Fig. 3). These projections 35 extend peripherally for a distance greater than the peripheral length of the radial bores 2I, and are formed on their inner surface with a contour corresponding exactly to the periphery of the shaft portion I0.

Side walls these side walls 36 and 31 rotate with the rotor I8 and form a tight flt therewith so as to prevent the leakage of fluid being pumped between the side walls and the rotor and shaft 4. n These side walls 36 and 31 extend outwardly beyond the inner periphery of cylinder 28 and are in extremely close fitting but slidable relation therewith so that the cylinder 28 may move slightly relative to the walls 36 and 31 as rotation of cylinder 2 8 takes place, this movement being necessary 1n order to allow cylinder 28 to remain eccentric relative to rotor I8. The frictional engagement between cylinder 28 and side cause the shifting of cylinder 28 during rotation is not great and because the parts areso designed `as to allow a minimum of friction at this point. In this way, the rotational frictional engagement between the rotor and vanes and the side walls 36 and 31 is eliminated and the friction of the pump is much less than the friction of vane pumps heretofore available in which the side walls, were stationary and in which the cylinder was likewise stationary relative to the rotor and vanes thereon.

As a result of the foregoing construction, it will be seen that when the rotor I8 is rotated in4 a direction clockwise'of Fig. l, and with the shift ring 30 in the position shown in. Fig. 1, fluid being pumped will be sucked in at conduit 24 and will be forced out at conduit 22 with very high. efiiciency of pumping, cylinder 28 rotating with the rotor -I8 by reason of the very low rolling friction imposed between cylinder 28 and rollers 29 and between rollers 29 and shift ring 30.4

General vAs seen in Fig. 2, shaft 4 terminates short of the extreme left-hand portion of the casing I the end of the shaft away from the driving end has not been accessible.

In order to prevent oil or other'iluid being pumped from traveling along shaft portion I0 in excessive amounts, the grooves 40 seen at the left hand of Fig. 2 are provided thereon, one of these grooves being placed on each side of the inlet and outlet ports 22 and 24. `When oil is the hydraulic medium being pumped, these grooves allow enough oil to escape to lubricate the bearing formed by members 28, 29 and 30 and the bearings 5 and 1. When a gas or nonlubricating liquid is being pumped, suitable means not shown may be provided for lubricating the various wearing parts and for maintaining the desired tight seal where required.

In order to retain the rollers 29 against excessive longitudinal movement, the cylinder 28 may be flangedas at 4| and the shift ring 38 may be similarly flanged as at 42.

From the foregoing, it will be seen that the inner race or cylindrical ring 28 absorbs the outward thrust of the vanes 21 and transmits it to the outer race or shift ring 30 and thence to the housing I. The ring 28 is positioned longitudinally by the side walls 36 and 31 which are positioned by the bearings 5 and 1, and as bearings 5 and 1 are adjusted by means of the member I6, ring 28 together with rollers 29 and shift ring 38 move longitudinally, shift lring 3|)4 being longitudinally slidable in housing I .but being normally retained against rotation'therein.

From Figs. 13 and 14 the magnitude of the clearances in several portions of the pump will be readily apparent. From Fig. 13 it will be seen that the clearance between the shaft portion 'I0 and the housing portion 6 therearound is of coni siderable magnitude so that this shaft portion I0 is free to rotate within the housing and is free to slide longitudinally therein upon adjustment of the bearings 5 and 1, and yet is sufficiently small that substantially no leakage therebetween occurs. The bearings 5 and 1 support the shaft of the pump in such a. manner that this shaft portion II) is free to rotate without binding even though a very large bending forces be applied to the pump shaft by reason of the pumping action. Fig. 13 further illustrates that there is no clearance between the outer race I I of bearing 5 and the housing there` around and that there is likewise no clearance between the inner race 8 and-fthe shaft portion. I0.

Fig. 14 illustrates that there is considerable ,clearance between the shift ring 38 and the housing I, so that the shift ring 30 is very free to move longitudinally upon the adjustment of the bearings 5 and 1. There is but slight tendency,

ofcourse, for the shift ring 3D to rotate and,

therefore, this clearance may be extremely large. It is likewise not essential that a fluid-tight seal be made between the shiftring 30 and the housing I, accordingly, the clearance at this point has beenshown as being even greater than the clear- I ance between shaft portion I 0 and the housing portion 6. Fig. 14 further shows that there is a rather small clearance between the outer race I4 of bearing 1 and the cover plate 2 so that the race I4 is free to move longitudinally during adjustment but is retained against rotation by reason of the frictional engagement of the cover plate 2. Fig. 14 shows that there is no clearance between the inner race I2 and the shaft portionl I3 and that there is also nc clearance between the side walls 38 and31 and the rotor I8, and that theY clearance between the pump ring 28 and the side walls 36 and 31 is extremely'small so that there is no leakage at this point.

Pilot pump' As is illustrated in Fig. 4, plate 38 referred to 43 carrying a. pilot pump which embodies the features of the main pump just described and which has a shaft 44, the end of which is flatted and is received in slot 39 in the left-hand end'of shaft 4. Shaft 44 is rotatably carried on taperedA bearings 45 in a manner similar to that in which shaft 4 of the main pump is journaled, an adjusting member 46 being provided as before for taking up the wear of these vbearings 45. Shaft 44 integrally carries a rotor 41. Four pumping the general construction is similar. to that described above in connection with Figs. 1 to 3 withthe difference that the cylinder or ring 28 rolli above may be removed and replaced with a plate ingly engages four spaced rollers 55 which are -rotatable about xed pivot points.. Theserollers 55 are in the form of hollow cylinders forming the outer raceof a needle bearing which has rolling needle bearing elements 56 which vroll upon an inner race 51 which is fixedly carried by, as by shrinking, a pin 58 which is flxedly mounted between a pair of annular side members 59, as by means of nuts 60, the intermediate portion of pin 58 being enlarged so as to form a spacer for n the annular plates 59. The annular plates 59 are provided with a pair of oppositely disposed fixedly attached longitudinal side ,members 6I againstwhich the shifting rods 33 and 34 for shifting the cylinder 2.8,* engage The members 59 and 6I form a shift ring for varying or reversing the delivery of the pump.. The members 59/ are atted at 82 at their top and bottom, these-- sponding flatted portions 32 on thev pumphouschambers are formed by four radial vanes 41e disposed similarly` to the vanes 21 of the main pump ,and operating in a similar manner. -Th'e rotor 41 fixedly carries the side walls 41a and 41h which correspond-to the side walls of the main pump.A 'I'he sidewall 41a is xedly mounted upon shaft V44v as yby being shrunk thereupon.

The left-hand side plate41b is integral With a sleeve 41d which is flxedly carried-on shaft 44 as by shrinkage thereupon, and the porting is accomplished by locating the ports 41e outside of the shaft 44a., in the sleeve 41d. These ports 41e communicate with the right-angled ports 41j in the rotor.` Thus, even though pump shaft 44 be small in diameter so that porting through it would so weaken it as to ldestroy its supporting function, porting is accomplished in a manner generally similar to that 4shown in Fig. 2. ,Valving-is accomplished in the same manner for`4r 'the main pump of Figs. 1 to 3.

atted portions slidably cooperating with correing I, as before, whereby by shifting rods 33 and 34 transversely, the eccentricity of cylinder 28 is varied without respect to rotor I8.

As a result of the foregoing construction, the

. cylinder or ring 28 is free to rotatewith the rotor,

there being `rolling friction at the points where cylinder 28 contacts the rollers' 55, and correspondingly rolling friction between the roller's 55 andthe needle elements 56 and between the needles 56 and the inner races 51 which are 'I'he vanes ofthe pilot pump carry with them f a cylinder 48 which :ls the inner race of a ball i bearing (as distinguished from the roller bearl mg usedfm the main pump) having bans 49 rollingly'engaging an outer raceor shift ringV 50 which is transverselymovable in the rpilot pump casing 5I by'means of rods 52 in a manner identical with that described above forthe main pump. As illustrated in Figs. 4 and 5; the

shift ring 58 of the pilot pump is shifted so as to deliver reversely from thermain pump.l For example,'assuming clockwise rotation ofthe rotor 41.01 the pilot pump (as viewed" in Fig. 5), .the pilot pump will .suck in uld through the upper conduit 58and will deliver fluid under pressure through the lower conduit 54 of Fig. 4. It will thus be seenv .that the pilot pump can have itsdelivery adjusted both in amount and in direction, irrespective of the delivery vof the main pump. v It will further be seen that the pilot pump operates inthe same -manner as the main pump and that its delivery may be varied from a maximum to zero in either direction in iinnitely small increments by shiftingthe shift ring 5l),V

just as in the case of the main pump.

Modification with stationdrly pivoted rollers In the modiiied forms shown inFigs. .6 and 7,

- screws 85 and the retaining ring 66. .The left other apparatus to be driven, since the 'stationary pintle occupies the space occupied by the left- V hand portion ofthe rotor shaft in Figs. l to 3. g As shown in Figs. 8 and 9, the rotor-carrying shaft 4 is journaled in the end plate 2a by means of oppositely directed roller thrust bearings 63.

` The right hand rotor side vwall 36a. `is integral with tnedriving .shaft 4 and is pinned to the rotor I8a by means of cap screws 64. The lefthand side wall 31u is flxedly attached to and carried bythe rotor Ica bymeans of the. cap

hand end of the housing ia is closed by amember Gawhich has a angedpcrtion 6b which.`

forms the left-hand end wall for the pump` A stationary pintle 61 is slidably but tightly .mounted in the casingmember 6a andhas a somewhat reduced portion extending through an axial 4bore inthe rotor I8@ with an extremelyclose but slidable t. .The rotor is journaled upon' the pintle'il by means of ,the tapered roller bearings 88 and 59. The left handroller bearing 69 -has its outer race '10 clamped between the ring 68 and the rotor I3a 4and its inner race 'II bearing .y

on'the Vleft hand against aV ring 12 which bears. against the inwardV face 13 of member. 5a. The right hand roller bearing 68 has its outer race 14 medly held between\the side wall- 3lia and the rotor I8a in ay suitable recess in the latter, and

'ting against the ring 12 which in turn abuts against and is positioned by the inward end 13 of the member 6a.

In order to pull the pintle 61.1eftward1y to make this adjustment, its left-hand end is provided with a threaded portion -which extends leftwardly of member 6a and on which is thread edly 4received an adjusting nut 11 which engages the outward face 18 of member 6a, and which .is split on one side and adapted to be locked against rotation by tightening a bolt 19 on the split side. Tightening of lbolt 19 draws the two split halves into locked relationship with respect to the threads on the end of the pintle 61 and prevents rotation of the nut 11 with respect to the pintle 61. Thus, by loosening locking bolt 19, turning nut l11 up on the pintle 61 until the clearance or wear has been taken vup, and tightening the locking bolt 19, the pintle is adjusted leftwardly and is xedly positioned in its adjustment.

In order to prevent the pintle from rotating, a slot 80 may be provided in its end portion, this slot engaging a suitable key (not shown) carried by the member 6a. The end of the pintle is protected by a cap plate 8| carried by the member 6a. A drainage port 82 may be provided in cap plate 8| for carrying ofi oil which escapes alongthe pintle Vto the space in the plate 8|.

The pintle 61 is cylindrical and is provided with four collecting'bores 83 which extend parallel to the axis 'of the pintle, and at the left-hand end of these bores 83 with four radial bores 84, the upper two of which extend into communication with a conduit 22a in the member 6a, and the lower two of which extend into similar communication with a conduit 24a. Either of .conduits 22a or 24a is adapted to function as an inlet or as an outlet conduit.

The valving of the pressure and suction chambers formed between the rotor |8a and the ring 28 is accomplished as follows. The pintle 61 is cut away adjacent the radial ports |9a in the rotor |8a, in the manner indicated in Figs. 8 and 9. This cutting away involves cutting radially inwardly on the surface of the pintle 61 so as to form a cross-shaped cross-section having two projections 85 which are adapted to seal the horizontal ports |9a which are designated E in Fig. 9. The vertical projections 86 are flatted on their outward face so as to allow free communication between all of the upper ports A or between all of the lower ports D and yet to exert a reinforcing action so that the pintle 61 is not appreciably weakened at this point. Thus, for example, the upper ports A may act as suction ports while the lower ports D act as pressure ports and the ports E are sealed ol so as to separate the discharge'side of the pump from the intake side. It will be understood, of course, that the ports are successively shifted by their engagement with the projections 85 as the rotor |8a rotates. al1 of the radial ports A are mcommunication pump. An annular passageway 94 which has its- It will further be seen that u with one another and in communication with either of the upper axial bores 83, and that the same is true of all of the radial ports D.

Modification with valuing through side wall of rotor In Figs.' 10 to 12, there is portrayed a modication of the invention wherein the 'valving of the pump chambers is effected through the side plate of the pump. The pump arrangement is in general along the lines of that in the embodiment of Figs. 1 to A3, the rotor I8b being integral with the pump shaft 4b which has an enlarged portion4 |3b journaled within a bearing 1b, and a reduced left-hand portion lub which is journaled in a bearing 5b. Bearing 5b is carried within a member 6c which is bolted to the main pump casing Ib by bolts 3b. The bearings 1b and 5b' are adjusted by a member I6 in thesame manner as that described above in connection with Figs. 1 to 3.

The rotor |8b has the radially extending ports |9b which correspond to the ports I9 in Figs. l to 3 and which merge with horizontal axial ports 81 which connect with coaxial ports 88 formed in the left-hand side wall 31h which is xedly and tightly secured to the rotor |8b asbefore.

Ports 88 extend outwardly through an annular boss 89 which is integral with side wall 31b and which is slidably received in an annular lgroove 90 formed in a stationary collecting-plate 9| xedly mounted between the-cap plate 6c and ,the casing Ib, the rightward edge of plate 9| being indicated as 9| b.

'I'he plate 9| serves to take off the intake and discharge and to keep the intake separate'from the discharge'l In order to accomplish this, the plate 9| has a generally radially extending passageway 92 which is in communication with the lower ports 88, and a similar passageway 93 in its upper portion which is in communication with the upper ports -88. Passageway 93 at its outward portion is in communication with conduit 95 while passageway 92 is in similar communication with a conduit 96, conduits 95 and 96 being formed in the cap plate 6b and being adapted to function either as inlet or outlet conduits, depending upon the direction of delivery of .the

center line coincident with the groove 90, at all times connects passageways 92 and 93 with the upper and' lower ports 88, respectively.

Separation of the inlet side of the pump from the outlet side is accomplished by theprovlsion of a pair of sealing members 91 adapted to seal the two ports 88 which are horizontal. As indicated in Fig. 12, these members 91 are cup-shaped and have a. flat rightward sealing face and are yieldingly pressed into engagement with the rotating plate 31h by aspring 98 which is interposed between the member 91 and a cup-like receiving member 99 mounted in a wall 9|a of the plate member 9|. The sealing member 91 is Vtightly but slidably received within the member 99 so that a seal exists at all times therebetween. Thus member 91 ls free to move relative to xed plate 9| during the longitudinal adjustiment of the rotor |8b by means of the member I6 to take up wear of .the bearings thereof, and at the same time to maintain perfect sealing contact over the horizontal ports 88 and to maintain a perfect seal between the passageways 93 and 92. The sealing members 91 are disposed in such manner as to cover the groove 94, as is indicated in Fig. 11 and thus to prevent pressure liquid from intermingllng with the suction liquid.

The modification shown in Figs. 10 to 12 is particularly advantageous where it is desiredto' use a pump shaft of small diameter where the introductionof ports inthe pumpshafl?. asin Fig. 2,5would.'unduly weaken the shaft. Infthe modication shown in Figs.I -to l2, valving is carried out exclusively through the side walls'of the pump'and outwardlyof the pump shaft sol that it is not'necessary to bore the pump shaft.

This construction is particularly advantageous in thecase of small pumps such as pilot pumps.

tion of vane pumps heretofore produced. It will further beseen that the invention' provides for the adjustment of the pump to take ,up wear by a single simple adjusting step.

` Numerous vother vadvantages of the ypump of the present invention :will be obvious to those skilledin the art. Y I wish it to be understoodv that I intend to innal movement of said shaft vto maintain the 'same working relationship therebetween as existed .prior to adjustment of said bearing means on said, shaft. i 2. A vane pump comprising shift ring supported within said h'ousing for movement transversely with respect Vto the axis ofV saidhousing and forming the outer race-of an anti-friction bearing, a cylinder ring positioned within said shift ring and forming the inner 'race of the anti-,friction bearing, a rotorpositioned within said cylinder ring normally ec- -centrically With'respect thereto,.a plurality `of vanes extending from said rotor into engagement with said cylinder ringto form a plurality of compression chambers, bearing'means posiof said bearing means comprising an ,inner race,

clude as within my invention such modifications and adaptations thereof as will be obvious to' those vskilled in the art and as `fall within the terms or the spirit of the appended claims.

`Having thus fully described `my invention, what I cla-im as new `and desire to secure by Letters Patent is: A

01. A vane pump comprising a pump housing, a` support member carried within said housing and forming the outer race of an anti-friction I bearing, a cylinder ring positioned within said support member and forming the inner race of the anti-friction bearing, a plurality of rotating bearing members disposed between saidsupport member and said 'cylinder ring to permit free rotation of said cylinder ring, a rotor positioned within said cylinder ring normally eccentrically with respect thereto and forming a fluid working space'therebetween, said working space having uid inlet and outlet ports therefor, means to rotate saidrotor, a plurality of vanes extending' between'said rotor andsaid cylinder ring, a shaft normally'xedly positioned in-said housing Vbut axially adjustably lmovable therein and extending within said rotor normally eccentrica-ily with respect to saidcylinder ring,` bearing4 means carriedjwithin opposite'faces of said rotor `and upon said shaft forfsupportin'g the'rotorluponl said shaft, 'each of isaid bearing means `comprising an outer' race', 'anfinner' race anda` plui ralityof ,rotary rbearing elements, endplates se-l cureditosaidrotor for engaging said cylinder ring and for securing said shaft bearing means within said rotor, means extending through said housing to engage said support member for shifting the sa-me transversely of the axis of said cylinder ring to thereby change the eccentricity between said cylinder ring and said rotor, means for axially moving said shaft, and

means engaging the inner races of the bearingl means on said shaft to cause relative movement between saidinner and outer races longitudinelly-with respect to each other and with respect to the axis of the shaft upon longitudinal movement of theV shaft to reduce the clearance between the elements of said bearing means on said shaft; said rotor, said cylinder ring and 'said support member following thel longituditioned Withinoppositesides of said rotor, each races of saidbearing ,means and said cylinder ring, an end wall for said housing, a. rotor supporting shaft supported in said. end wall normally eccentrically with respect to said cylinder ring, said shaftextending throughsaid bearing means in said rotor to support said rotor, an`

end wall for the end `of saidhousng Which is opposite said shaft having bearing means `therein, a shaft extending fromr the rotor end plateA adjacent said end wall andbeing supportedin said last-named bearing means, port means .ex-

tending through saidrotor in communication with said chambers, portV means .extending longitudinally through said support shaft and communicating with said rotor port means, and-port means in the end wallsupporting said support shaft communicating with said portmeansin said shaft for providing an inlet and an outlet to said chambers. l s

3. In a vane pump a housing providing a chamberltherein, a shaft supportedby afwall of saidv housing and extending into .the .chamber providedbysaid housing,l a' rotor, bearing means positioned in opposite sides of said rotor, each of said bearing means comprising an in-` ner race, an outer race and a. plurality ,of rotary bearing elements vtherebetweenthecle'arance between said bearing elementsV beingadjustable by displacement of said bearing. races relative to each other, meansY for retaining the outer races'of said bearing means 'in said rotor, means engaging the inner races of said bearing means to cause relative movementbetween said inner and outer races upon, longitudinal .movement of said shaft, said shaft being-movable longitudinally xwithmrespect to the 'axis thereofY to cause saidrelatvemovement between A bearing means but sumciently small that a liquid seal is provided therebetween by means of the lubricating liquid provided within the pump A whereby said rotor is oatingly carried upon said shaft. a rotatable cylinder associated with'- said rotor normally eccentrically with respect thereto, vanes between said rotor and said cylinder, iluid flow passages for conducting uid to and from said cylinder, and end plates secured to said rotor for engaging said cylinder which rotates therewith. the clearance between saidv a housing hav-- ing an internal chamberlopenat both ends, a'

prevent escape of high pressure fluid from said cylinder.

4. In a vane pump a housing providing a chamber therein, a shaft supported by a wall of said housing and extending into the chamber,

provided by said-housing, a rotor, bearing means positioned in opposite sides of said rotor, each of said bearing means comprising an inner race, an outer race and a plurality of rotary bearing elements therebetween the clearance between said bearing elements being adjustable by displacement of said bearing races relative to each other, means for retaining the outer races of said bearing means in said rotor, means engaging the inner races of said bearing means to cause relative movement between said inner and outer races upon longitudinal movement of said shaft, said shaft being .movable longitudinally with respect to the axis thereof to cause said relative movement between said inner and outer races to thereby reduce the clearance between said bearing elements and races to zero and maintain a concentric clearance area between said shaft and said rotor greater than the total clearance provided in said bearing means but sufllciently small that a liquid seal is provided therebetween by means of the lubricating liquid provided within the pump whereby said rotor is floatingly carried upon said shaft, a rotatable cylinder associated with said rotor normally eccentrically with respect thereto, vanes between said rotor and said cylinder, fluid ow passages for conducting fluid to and from said cylinder, end plates secured `to sai'd rotor for engaging said cylinder which rotates therewith, the clearance between said end plates and said cylinder being less than the clearance between said rotor and said shaft whereby a fluid tight sliding relationship is provided between said end plates and said cylinder without dependence upon a liquid seal therebetween by means of the lubricating liquid to prevent escape of high pressure fluid from said cylinder, and rotary bearing elements in engagement with said cylinder for supporting the same, said last-named rotary bearingk elements having an outer race in engagement with said housing shiftable within said housing to change the eccentric relationship between said cylinder and said rotor, the total clearance between said lastnamed rotary bearing elements, said cylinder and said last named outer race being substantially zero to maintain accurate alignment of said cylinder between said end plates and ac'- curate concentricity or eccentricity of said cylinder relativeto `said rotor, while the bearing clearance between said last named outer race and said housing is greater than the clearance between said rotor and said shaft to permit completefreedom of movement of said last named outer race within said housing longitudinally and transversely with respect to the axis of said shaft when shifting of the outer race to thereby change the eccentric relationship between said cylinder and said rotor and when adjusting the clearance of the bearing elements supporting said rotor.

5.A pump comprising a housing, a rotor ro- I tatably mounted therein means to rotate said rotor, a pump Cylinderring surrounding said rotor and normally eccentric thereto, vanes between said cylinder ring and rotor said cylinder ring and rotor forming a fluid working chamber therebetween, fluid inlet and outlet means for said working chamberf shift ring means surrounding said cylinder ring, rotatable bearing means disposed between said cylinder ring and said shift ring for allowing said cylinder ring vto freely rotate within said shift ring and with said rotor, said shift ring engaging said housing so as to be longitudinally and transversely movable therein with respect to the axis of said shift ring but normally non-rotatable therein, a nonrotatable shaft for said rotor carried by said housing and movable longitudinally with respect therewith and for retaining rotor bearing means in said rotor, a bearing on said shaft on each side of said rotor positioned within said rotor and retained therein by' said side wall means, each of said bearings comprising an in .ner race engagingsaid shaft and an outer race engaging said rotor, the clearance of said bearings being adjustable by axial displacement of said races with respect to each other, said outer races being flxedly positioned in said rotor against longitudinal movement therein, and means engaging said inner races and engaged by said shaft formoving said inner races longitudinally toward said outer races whereby to take up wear and slack in said bearings and to simultaneously position longitudinally said rotor, said side wall means, said cylinder ring and said shift ring within said housing and axially upon said shaft upon lon- WARREN R. TUCKER. 

